JPH09512616A - Fuel injection device used for internal combustion engine - Google Patents

Fuel injection device used for internal combustion engine

Info

Publication number
JPH09512616A
JPH09512616A JP8524601A JP52460196A JPH09512616A JP H09512616 A JPH09512616 A JP H09512616A JP 8524601 A JP8524601 A JP 8524601A JP 52460196 A JP52460196 A JP 52460196A JP H09512616 A JPH09512616 A JP H09512616A
Authority
JP
Japan
Prior art keywords
valve
chamber
pressure
valve member
injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
JP8524601A
Other languages
Japanese (ja)
Inventor
ポッツ デートレフ
レヴェンツ ギュンター
マイアー ラルフ
カムプマン シュテファン
ゴルドン ウーヴェ
クレー アンドレアス
ロドリゲス−アマヤ ネストル
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of JPH09512616A publication Critical patent/JPH09512616A/en
Abandoned legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/06—Other fuel injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F02M61/045—The valves being provided with fuel discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Abstract

(57)【要約】 内燃機関に用いられる燃料噴射装置であって、燃料高圧ポンプ（１）が設けられており、この燃料高圧ポンプ（１）が低圧室（３）から圧送管路（５）を介して高圧集合室（コモンレール）（７）へ燃料を圧送する。この高圧集合室（７）は高圧管路（９）を介して、燃料供給されるべき内燃機関の燃焼室に突入した個々の噴射弁（１１）に接続されている。この場合に噴射弁（１１）における可変の噴射横断面を可能にするために、この噴射弁は外方に向かって開く弁部材（１７）を備えた噴射弁として形成されている。この弁部材の制御可能な、燃焼室の方向での開放行程運動を介して、噴射弁（１１）における可変の噴射横断面が調節可能である（第１図）。 (57) [Summary] A fuel injection device for use in an internal combustion engine, comprising a high-pressure fuel pump (1), the high-pressure fuel pump (1) extending from a low-pressure chamber (3) to a pressure-feeding conduit (5). Fuel is pressure-fed to the high-pressure collecting chamber (common rail) (7) via the. This high-pressure collecting chamber (7) is connected via a high-pressure line (9) to an individual injection valve (11) which projects into the combustion chamber of the internal combustion engine to be fueled. In order to allow a variable injection cross section in the injection valve (11) in this case, this injection valve is designed as an injection valve with a valve member (17) which opens outwards. Via a controllable opening stroke movement of the valve member in the direction of the combustion chamber, a variable injection cross section at the injection valve (11) is adjustable (FIG. 1).

Description

【発明の詳細な説明】 内燃機関に用いられる燃料噴射装置 背景技術 本発明は、請求項１の上位概念部に記載の形式の、内燃機関に用いられる燃料 噴射装置から出発する。このような形式の燃料噴射装置は、専門誌「ＡＴＺ／Ｍ ＴＺ ゾンダーヘフト・モトーア・ウント・ウムベルト（Sonderheft Motor und Umwelt）、１９９２年、第２８頁〜第３０頁に記載されている。この公知の燃 料噴射装置では、高圧ポンプにより燃料が低圧室から高圧集合室（Common-rail ）へ圧送され、この場所で機関回転数とは無関係に噴射のために提供される燃料 高圧レベルが形成される。高圧集合室からは、噴射個所の数に相当する複数の高 圧管路が導出されていて、燃料供給されるべき内燃機関の燃焼室に突入した個々 の噴射弁に通じている。この場合、高圧管路は噴射弁において、弁部材を開放方 向で負荷する圧力室に開口している。「内方に向かって開く噴射ノズル」として 形成された噴射弁の弁部材の開放行程運動の制御は、３ポート２位置弁によって 行われる。この３ポート２位置弁は、高圧管路から分岐した部分管路に挿入され ている。この部分管路は、弁部材を閉鎖方向で負荷する制御室に開口している。 噴射弁の弁部材に設けられた、 閉鎖方向に作用する受圧面は、開放方向に作用する受圧面よりも大きく形成され ているので、弁部材は、制御室が高圧で負荷された状態において、弁座に押圧さ れて保持される。噴射を行いたい場合には、３ポート２位置弁が制御室を燃料タ ンクに接続するので、制御室内の圧力は燃料タンクに放圧され、弁部材に作用す る開放力は、弁部材を弁座から持ち上げるために十分となるので、燃料は噴射開 口を介して噴射され得る。噴射弁を閉鎖するためには、制御室が再び高圧管路に 接続される。噴射経過を制御するためには、３ポート２位置弁と制御室との間の 接続管路に絞りが挿入されており、噴射終了時に弁部材を迅速に閉鎖するために は、制御室の方向で開く逆止弁が挿入されている。 この公知の燃料噴射装置には、次のような欠点がある。すなわち、この場合に 使用される噴射弁を用いても、可変の噴射横断面が可能とならない。このことは 特に低い回転数および低い負荷において、高圧集合室内の極めて高い噴射圧に基 づき、極めて短時間の噴射時間を生ぜしめる。このような極めて短時間の噴射時 間は燃焼室における燃料調整に不都合な影響を与え、ひいては燃焼の品質にも不 都合な影響を与える。 さらに、噴射過程を制御するために複雑な３ポート２位置弁を使用することは 極めて不経済であるので、公知の燃料噴射装置の製造は手間とコストがかかる。 発明の利点 請求項１の特徴部に記載の本発明による、内燃機関に用いられる燃料噴射装置 には、従来のものに比べて次のような利点がある。すなわち、公知のコモンレー ル型の噴射システムを改良して、噴射弁における可変の噴射横断面により、常時 提供される高い噴射圧の利点を十分に利用することができるようになる。このこ とは、外方に向かって開く弁部材を備えた噴射弁の使用により簡単に可能となる 。この弁部材の、調節可能な開放行程を介して、可変の噴射横断面が制御可能と なる。 外方に向かって開く構造の噴射弁はこの場合、無段階に制御可能であってよい 。このためには、弁部材行程に関連して開制御可能な、閉鎖ヘッドと弁座との間 の環状ギャップが噴射横断面を形成している。噴射横断面はシール横断面に前置 されたスプール弁によって制御されると有利である。このスプール弁の弁部材は 、たとえばジオメトリ的に正確に規定された複数の噴射開口を有している。これ らの噴射開口の配置により、開放行程に関連して、ハウジングとの重なりからの 噴射開口の進出時に精密な噴射横断面を調節することができる。これらの噴射開 口は、軸方向で上下に位置する２つの噴射孔列によって形成されていると有利で ある。両噴射孔列は弁部材の開放行程時に順次に開制御される。こうして、規定 の弁部材行程により、燃焼室寄りの下側の噴射孔列だけを開制御し、すなわちた とえばまず全噴射横断面の１／２だけを開放することが、構造的に簡単に可能と なる。この場合、弁部材には、この規定の中間位置における弁部材の滞留を可能 にする制御手段が設けられている。しかし択一的に、さらに多くの噴射孔列と、 弁部材の規定の滞留位置とを設けることも可能である。このような噴射孔は環状 ギャップに比べて、噴射したい燃料の噴流方向および噴流経過が一層良好に調節 可能となるという利点を持っている。 このように、有利には５０％の減じられた噴射横断面だけを開制御することは 、特に小さな回転数の場合や、燃料供給されるべき内燃機関の部分負荷領域にお いて有利である。すなわち、高い噴射圧にもかかわらず噴射時間を、好都合な燃 料調整のための最適な値に調節することができるという利点が得られる。 こうして、本発明による燃料噴射装置では、自由に設定可能な噴射時機におい て可変の噴射圧と、可変の噴射横断面との組合せに基づき、燃料噴射を内燃機関 の各運転点に合わせて最適に調整することができる。噴射圧の変化は公知の形式 で高圧集合室の圧力制御によって行われる。 本発明のさらに別の利点は、噴射弁における噴射過程を制御するために単純な ２ポート２位置弁を使用することにより得られる。この２ポート２位置弁は電磁 石によって操作されると有利である。しかしこれに対 して択一的に、機械的、ハイドロリック的またはニューマチック的な操作もしく は公知先行技術に基づき公知の３ポート２位置弁も可能である。 噴射弁の弁部材に加えられる閉鎖力は、ばね力または噴射システム内の高圧に よって形成することができる。このためには、２ポート２位置弁における種々様 々な制御コンセプトが可能である。すなわち、電磁石は２ポート２位置弁を、た とえば無電流状態で開いた状態または閉じた状態に保持することができるので、 弁部材の、燃焼室側の端部を収容する戻し室は、噴射弁の閉じられた状態におい て無圧状態となるか、または圧力負荷されている。下側の噴射孔列だけを開制御 する規定の位置に弁部材を保持する中間ストッパは、ハイドロリックストッパ（ 閉制御される孔）として形成されているか、または機械的なストッパ（第２のば ねの作動）として形成されていると有利である。閉鎖力としてシステム圧を使用 する場合、弁部材に設けられた、ハイドロリック的に調節可能な閉鎖ヘッドが特 に有利である。この閉鎖ヘッドの、ハイドロリック的に調節可能な軸方向の延び を介して、弁部材の無段階調節可能な行程距離が可能となる。弁部材の開放行程 運動のための制御量としては、噴射システム内の燃料高圧または２ポート２位置 弁の位置を利用することができる。 このような種々の制御コンセプトは、燃料供給され るべき内燃機関に課せられる前提条件に関連して、種々異なる利点を有している 。したがって、以下においては４つの実施例だけを詳しく説明する。これらの実 施例の特徴は互いに入れ替え可能であり、かつ互いに組み合わせ可能となる。本 発明の対象の別の利点および別の構成は、実施例の説明、図面および請求の範囲 に記載されている。 図面 以下に、内燃機関に用いられる本発明による燃料噴射装置の４つの実施例を図 面につき詳しく説明する。 第１図は、噴射弁の弁部材におけるハイドロリック閉鎖力を利用する、無電流 状態で開く２ポート２位置電磁弁を備えた第１実施例を示しており、第２図は、 第１図に示した噴射弁の噴射開口の範囲の拡大断面図を示しており、第３図は弁 部材におけるハイドロリック閉鎖力を利用する、無電流状態で閉じた２ポート２ 位置弁と、ハイドロリック的に調節可能な閉鎖ピストンとを備えた第２実施例を 示しており、第４図は、無電流状態で開いた２ポート２位置電磁弁において閉鎖 力が閉鎖ばねによって加えられる、第３実施例を示しており、第５図は、２ポー ト２位置電磁弁が無電流状態で閉じられていて、閉鎖力が２ばね装置によって形 成される、第４実施例を示している。 実施例の説明 第１図に示した第１実施例による、内燃機関に用い られる燃料噴射装置は、燃料高圧ポンプ１を有している。この燃料高圧ポンプ１ は低圧室３、有利には燃料タンクから圧送管路５を介して高圧集合室７へ燃料を 圧送する。この高圧集合室７からは、噴射個所の数に相当する複数の高圧管路９ が延びていて、燃料供給されるべき内燃機関の燃焼室に突入した個々の噴射弁１ １に通じている。噴射弁１１は弁ボディ１３を有しており、この弁ボディ１３は 中心の孔１５を備えている。この孔１５には、ピストン状の弁部材１７が軸方向 で案内されている。この弁部材１７はその燃焼室側の端部で、孔１５から突出し かつ弁閉鎖部材を形成する閉鎖ヘッド１９を有している。第２図に拡大して示し た閉鎖ヘッド１９は弁ボディ１３に面した側に、シール縁部を形成するシール面 ２１を有している。このシール面２１により、閉鎖ヘッド１９は弁ボディ１３の 燃焼室側の端面に配置された弁座面２３と協働する。閉鎖ヘッド１９は弁部材１ ７のピストン軸部に比べて増大させられた横断面で、孔１５の、直径の拡大され た部分に突入していて、こうして燃焼室とは反対の側の端面２５で、孔１５内に 形成された圧力室２７を仕切っている。この圧力室２７は孔１５の壁と弁部材軸 部との間の環状ギャップ２９を介して、弁ボディ１３に設けられた燃料供給通路 ３２にまで延びている。この場合、閉鎖ヘッド１９に設けられた、増大させられ た横断面はスリーブ２６によって形成されると有利で ある。このスリーブ２６は閉鎖ヘッド１９に固定されていて、孔１５の壁に沿っ て密に軸方向で滑動する。可動の弁スライダを形成する前記スリーブ２６には、 軸方向で上下に位置する２つの噴射開口列（噴射孔列）２８が設けられていると 有利である。この噴射開口列２８は、孔１５からの弁部材１７の進出時にまず最 初に第１の下側の、燃焼室寄りの列が、規定のアイドリング行程後に開制御され 、それに対して上側の第２の列は引き続き弁部材行程が実施された後でしか、弁 ボディ１３の孔壁との重なり状態から解放されないように配置されている。環状 ギャップ２９から噴射開口２８に燃料を供給するためには、さらに弁部材１７と スリーブ２６との間に切欠き３０が設けられている。 環状ギャップ２９は、閉鎖ヘッド１９とは反対の側の方向で、ハウジングウェ ブ３１によって仕切られる。このハウジングウェブ３１では、孔１５の直径が減 少しており、この場合、弁部材１７は密に滑動可能に案内されている。このハウ ジングウェブ３１に続いて、燃焼室とは反対の側には、孔１５の新たな直径拡大 部により形成された背室３３が設けられている。この背室３３には、弁部材１７ の、燃焼室とは反対の側の端部が突入している。背室３３はハウジングカバー３ ５によって閉じられている。弁部材の、燃焼室とは反対の側の端部は、操作部分 を形成する閉鎖ピストン３７を有している。この閉鎖ピストン３７は背室３３の 壁に沿って密に滑動し、こうして背室３３を、戻し室３９を形成する下側の、燃 焼室側の部分室と、放圧室４１を形成する上側の、燃焼室とは反対の側の部分室 とに分割している。この場合、閉鎖ピストン３７の下側の、燃焼室側の環状端面 は、閉鎖方向での弁部材１７の受圧面４３を形成している。この受圧面は閉鎖ヘ ッド１９に設けられた、開放方向に作用する端面２５よりも大きく形成されてい る。 噴射弁１１に燃料を供給し、かつ外方に向かって開く弁部材１７の開放行程運 動を制御するためには、高圧管路９が噴射弁１１の近くで２つの部分管路に分岐 されている。両部分管路のうち、第１の部分管路４５は絞られずに燃料供給通路 ３２に開口し、さらに圧力室２７に開口している。第２の部分管路４７は背室３ ３の戻し室３９に開口している。この場合、第２の部分管路４７は、この第２の 部分管路に挿入された、電磁石によって制御可能な２ポート２位置弁４９により 閉鎖可能である。 背室３３の上側の放圧室４１を放圧するためには、この放圧室４１から放圧管 路５１が延びていて、低圧室３に通じている。 開放行程運動を制御するためには、下側に位置する戻し室３９から閉制御管路 ５３が導出されている。閉制御管路５３は、この閉制御管路が閉鎖ピストン３７ の行程運動時に、この閉鎖ピストン３７によって閉鎖 可能とならないように背室３３に開口している。さらに閉制御管路５３には、２ ポート２位置弁として形成された制御電磁弁５５が挿入されている。この制御電 磁弁５５は閉制御管路５３を低圧室３に向かって開放するか、もしくは閉鎖する 。制御電磁弁５５は複数の噴射弁のために使用可能であってよい。 さらに、戻し室３９からは、絞り個所５７を有する絞り管路５９が低圧室３に 導出されている。この絞り管路５９の開口部は、この開口部が規定の開放行程距 離の通過後に閉鎖ピストン３７によって閉鎖可能となるように戻し室３９に配置 されている。この場合、弁部材１７のこの開放行程位置は下側の噴射孔列の開制 御に相当する。 弁部材１７の最大開放行程距離を制限するためには、戻し室３９にストッパス リーブ６１が挿入されている。このストッパスリーブ６１の上側の環状面は、閉 鎖ピストン３７の受圧面４３と協働するストッパを形成している。このストッパ スリーブ６１は第２の部分管路４７と閉制御管路５３とのための貫通開口を有し ている。 第１図および第２図に示した第１の実施例による燃料噴射装置は次のように作 動する。 噴射弁１１の閉じられた状態において、２ポート２位置弁４９は開いている（ 電磁石は無電流状態）ので、高圧ポンプ１によって高圧集合室７に形成された燃 料高圧は背室３３の戻し室３９に伝播する。閉鎖ピストン３７の受圧面４３に作 用する高圧は、弁部材１７のシール面２１を弁座面２３に押圧する。噴射弁１１ を開放するためには、２ポート２位置弁４９（通電状態）が背室３３と高圧集合 室７との接続を遮断する。下側の戻し室３９内の高圧は絞り管路５９を介して減 圧される。この場合、この過程、ひいては弁部材１７の開放行程経過は絞り５７ によって調節することができる。弁部材１７に作用する閉鎖力の減少により、圧 力室２７に形成されて端面２５を介して弁部材１７に作用する開放圧は、弁部材 １７を弁座２３から持ち上げて、噴射開口２８を開放するために十分となる。 このときに弁部材１７はまず、閉鎖ピストン３７が絞り管路５９を閉鎖し、こ のときに閉じられた下側の戻し室３９がハイドロリックストッパを形成する程度 にまでしか摺動しない。この位置では、下側の噴射孔列が開制御されている。弁 部材１７の開放行程を継続させたい場合、制御電磁弁５５が閉制御管路５３を開 放して、下側の戻し室３９内の圧力が低圧室３へ放圧されるので、弁部材１７は 、閉鎖ピストン３７がストッパスリーブ６１に当接するまでの最大開放距離を達 成することができる。このときに弁部材１７は噴射開口２８の上側の第２の噴射 孔列をも開制御する。中間位置における弁部材１７の滞留を中止させたい場合に は、閉制御管路５３を直ちに開放することにより、迅 速な最大開放行程を達成することが可能である。 噴射弁１１を再び閉鎖するためには、２ポート２位置弁が再び開放されるので 、下側の戻し室３９では、閉制御管路５３が閉鎖された状態で再び燃料高圧が形 成される。この燃料高圧は弁部材１７を弁座２３に戻す。 第３図に示した第２実施例は、弁部材の開放行程運動の制御形式の点でのみ第 １実施例と異なっている。したがって、第２実施例の説明は当該構成部分に関し てのみ行う。同一の構成部分は第１実施例の場合と同じ符号を備えている。 高圧管路９から分岐されかつ下側に位置する戻し室３９に開口した第２の部分 管路４７には、絞り個所６３が挿入されている。さらに、戻し室３９からは、制 御管路６５が導出されている。この制御管路６５は低圧室３に開口していて、こ の制御管路に挿入された電磁制御式の２ポート２位置弁４９によって閉鎖可能で ある。 閉鎖ピストン３７は第３図の実施例では、２つの部分から形成されている。燃 焼室から遠い方の上側のピストン部分６７は、弁部材１７の、背室３３に突入し た端部に固く結合されており、燃焼室寄りの下側のピストン部分６９は弁部材軸 部に沿って軸方向で摺動可能に案内されている。両ピストン部分６７，６９の間 で取り囲まれた室は調節室７１を形成している。この 調節室７１は、低圧室３から燃料を供給される、調節室７１の方向で開く逆止弁 ７５を有する燃料管路７３を介して燃料で充填可能である。さらに調節室７１は 、燃料管路７３から分岐した、制御弁７９によって開放可能な部分管路７７を介 して、低圧室３へ放圧可能である。両ピストン部分６７，６９の間に緊縮された 圧縮ばね８１は、背室３３が放圧された状態で、両ピストン部分６７，６９をそ の出発位置へ移動させる。 第３図に示した第２実施例による燃料噴射装置は次のようにして作動する。 噴射弁１１が閉じられた状態で、制御管路６５に挿入された２ポート２位置弁 ４９は閉じられている（無電流状態）ので、第２の部分管路４７を介して燃料高 圧が戻し室３９内に形成される。この燃料高圧は下側のピストン部分６９を、弁 部材１７の閉鎖方向に負荷する。この閉鎖力は調節室７１の充填度に応じて直接 に、またはハイドロリッククッションを介して、弁部材固定の上側のピストン部 分６７に伝達されるので、弁部材１７は弁座２３に保持される。 噴射弁１１を開放するためには、２ポート２位置弁４９が開く（通電状態）の で、戻し室３９内の圧力は低圧室３へ放圧される。その結果、圧力室２７内の、 開放方向で弁部材１７に作用する圧力が、弁部材１７を弁座２３から持ち上げる ために十分となる。この場合、この開放行程運動は、ストッパスリーブ６１に下 側のピストン部分６９が当接するまで継続される。弁部材の可変の行程制御、特 に下側の噴射孔列だけを開制御する位置における弁部材１７の滞留は、調節室７ １の規定の充填により達成される。このためには、このハイドロック容積が最小 行程のためには燃料管路７３を介して完全に充填され、また最大行程のためには 制御弁７９を介して適宜に排出される。この場合、調節室７１の適当な充填によ り、複数の中間位置も可能となる。噴射弁１１の閉鎖は、２ポート２位置弁４９ を再び閉鎖することにより行われる。これにより、背室３３の戻し室３９内に再 び閉鎖圧が形成され、弁部材１７が弁座２３に戻される。 第４図に示した第３実施例は、弁部材１７に加えられる閉鎖力の作用形式の点 で、前記実施例とは異なっている。この場合、閉鎖力はばね力によって形成され る。このためには、弁ばね８３が背室３３に配置されている。この弁ばね８３は 弁部材１７の、燃焼室とは反対の側の端部に配置されたばね受け８５と、背室３ ３を燃焼室側で仕切る環状肩部８７との間に緊定されている。この弁ばね８３は 、圧力室２７内に形成される、弁部材１７を開放方向で負荷する燃料高圧に抗し て弁部材１７を弁座２３に接触した状態に保持する。背室３３からは、放圧管路 ５１が導出されている。この放圧管路５１は低圧室３に開口していて、この放圧 管路５１に挿入された２ポート２位置弁４９を介して 閉鎖可能である。さらに、背室３３と２ポート２位置弁４９との間では、高圧管 路９と背室３３との間の接続管路を形成する第２の部分管路４７が放圧管路５１ に開口している。この場合、本発明による燃料噴射装置の第３実施例では、第２ の部分管路４７に絞り個所５７が挿入されている。第４図に示した第３実施例に よる燃料噴射装置は次のようにして作動する。 噴射弁１１の閉じられた状態において、放圧管路５１もしくは第２の部分管路 ４７に配置された２ポート２位置弁４９は開いている（無電流状態）ので、背室 ３３には燃料高圧が形成され得ない。弁ばね８３は、圧力室２７に存在する、開 放方向で弁部材１７に作用する燃料高圧に抗して弁部材１７を弁座２３に保持し ている。噴射弁１１を開放するためには、２ポート２位置弁４９が、背室３３と 低圧室３との間の放圧接続を閉鎖するので、第２の部分管路４７を介して、背室 ３３内に噴射システムの燃料高圧が形成される。このときに、背室３３に突入し た弁部材部分に作用する、弁部材１７の開放方向における合成押圧力が、圧力室 ２７に生ぜしめられる押圧力と相まって、弁ばね８３の戻し力よりも大きく形成 されるので、弁部材１７は弁座２３から持ち上げられ、噴射開口を開放する。ま ず下側の噴射孔列だけを開制御する位置に弁部材１７を滞留させることは、たと えば弁ばね８３のプログレッシブな特性線または規定のアイドリング行程により 達成することができる。この場合、制御圧として高圧集合室の燃料高圧が使用さ れる。 噴射過程の終了時に噴射弁を閉鎖するためには、２ポート２位置弁４９が再び 低圧室３への放圧管路５１を開放するので、背室３３内の燃料高圧は迅速に放圧 され、弁ばね８３は弁部材１７を弁座２３に戻す。 第５図に示した第４実施例では、高圧管路９から出発した第２の部分管路４７ が直接に背室３３に開口しており、この場合、第２の部分管路４７は、この部分 管路４７に挿入された２ポート２位置弁によって閉鎖可能となる。背室３３の放 圧は、この背室から低圧室３へ導出された放圧管路５１によって行われる。この 放圧管路５１は第４実施例では、絞り個所５７を有している。 弁部材１７に加えられる閉鎖力もしくは戻し力は、２ばね装置によって形成さ れる。このためには、背室３３に突入した弁部材軸部で、燃焼室とは反対の側の 端部に配置されたばね受け８５と、背室３３を仕切る環状肩部８７との間に環状 段部８９が設けられている。ばね受け８５と環状段部８９との間には、第１の弁 ばね９１が緊定されており、環状段部８９と、ハウジング固定の環状肩部８７と の間には第２の弁ばね９３が緊定されており、この場合、第１の弁ばね９１のば ね剛性は、第２の弁ばね９３のばね剛性よりも小さく形成されている。この第４ 実施例では、第１の弁ばね ９１のばね力に抗して実施される弁部材１７の前行程運動を調節するために、ば ね受け８５のばね側の環状端面にスリーブ９５が固定されている。このスリーブ ９５の、ばね受け８５とは反対の側の端面は前行程運動の実施後に環状段部８９ に接触する。次いでスリーブ９５は、第１の弁ばね９１を遮断して、ばね受け８ ５と環状段部８９との間の固い結合を形成するので、引き続き開放行程が行われ ると、第２の弁ばね９３だけが作用する。このような中間位置における滞留は、 択一的にスリーブ９５なしでも達成することができる。この場合、残留行程にお いて、両弁ばねが有効となる。 第５図に示した第４実施例による燃料噴射装置は、次のようにして作動する。 噴射弁１１が閉鎖された状態において、部分管路４７に挿入された２ポート２ 位置弁４９は閉鎖されている（無電流状態）ので、背室３３は、規定の絞り個所 ５７を有する放圧管路５１を介して規定の圧力にまで放圧されている。弁部材１ ７は両弁ばね９１，９３のばね力により、圧力室２７内の圧力に抗して弁座２３ に接触した状態に保持される。噴射を行いたい場合、２ポート２位置弁４９が開 くので、背室３３には噴射システムの燃料高圧が形成され、この燃料高圧は第４ 図につき説明したように、弁部材１７を開放方向に運動させる。この場合、まず 第１の弁ばね９１の小さな ばね力に抗して、スリーブ９５が環状段部８９に当接するまで前行程が実施され る。この前行程は、弁部材１７に設けられた下側の噴射孔列を開制御するために 十分となる。この位置において、弁部材１７は２ポート２位置弁４９のタイミン グ制御により、背室３３内の一定の圧力を維持するために保持され得る。弁部材 １７に設けられた噴射横断面全体を開制御したい場合には、背室３３への圧力供 給が中断されないので、背室３３内の燃料圧は増大し、この場合、弁部材１７は 第２の弁ばね９３のばね力に抗してさらに、上側の第２の噴射孔列も開制御され る位置にまで移動させられる。 噴射弁１１を引き続き閉鎖するためには、２ポート２位置弁４９が再び閉鎖さ れるので、背室３３内の高圧は放圧管路５１を介して低圧室３へ放圧され、両弁 ばね９１，９３は弁部材１７を弁座２３に戻す。 ２ポート２位置弁４９の操作は全ての実施例において、電子制御装置（図示し ない）によって制御される電磁石によって行われる。この場合、電子制御装置は 公知の形式で、燃料供給されるべき内燃機関の多数の運転パラメータを処理する 。 したがって、「コモンレール（Common-Rail）」型の噴射システムの利点を、 外方に向かって開いた構造の噴射弁の利点と構造的に簡単に結び付けることが可 能となるので、自由に設定可能な可変の噴射開始および 噴射終了や可変の噴射圧が得られると同時に、燃料供給されるべき内燃機関の全 特性フィールドにわたって可変の噴射横断面を自由に調節することも可能となる 。この場合、この燃料噴射装置は２ポート２位置弁によって簡単に制御可能とな る。Detailed Description of the Invention             Fuel injection device used for internal combustion engine   Background technology   The invention relates to a fuel for use in an internal combustion engine of the type described in the preamble of claim 1. Depart from the injector. A fuel injection device of this type is available from the specialized magazine "ATZ / M". TZ Sonderheft Motor und Umberto  Umwelt), 1992, pp. 28-30. This known fuel In the fuel injection device, fuel is fed from the low pressure chamber to the high pressure collecting chamber (Common-rail ) And is provided here for injection at this location regardless of engine speed A high pressure level is formed. From the high pressure collection chamber, there are multiple high The individual pressure line is led out and rushes into the combustion chamber of the internal combustion engine to be fueled. Is connected to the injection valve. In this case, in the high pressure line, in the injection valve, open the valve member There is an opening in the pressure chamber that loads in the opposite direction. As an “injection nozzle that opens inward” The control of the opening stroke movement of the formed valve member of the injection valve is performed by the 3-port 2-position valve. Done. This 3-port 2-position valve is inserted in a partial line that branches from the high pressure line. ing. This partial line opens into the control chamber which loads the valve member in the closing direction. Provided on the valve member of the injection valve, The pressure receiving surface acting in the closing direction is made larger than the pressure receiving surface acting in the opening direction. Therefore, the valve member is pressed against the valve seat when the control chamber is loaded with high pressure. Is retained. When it is desired to inject fuel, the 3-port 2-position valve opens the control chamber The pressure in the control chamber is released to the fuel tank and acts on the valve member. The opening force to open the valve member is sufficient to lift the valve member from the valve seat, so fuel is injected and opened. It can be injected via the mouth. In order to close the injection valve, the control chamber must be put back into the high pressure line. Connected. In order to control the injection process, the 3-port 2-position valve and the control chamber A throttle is inserted in the connecting line to quickly close the valve member at the end of injection. Has a check valve that opens in the direction of the control room.   This known fuel injection device has the following drawbacks. That is, in this case Even with the injection valve used, a variable injection cross section is not possible. This is Especially at low engine speeds and low loads, the Therefore, an extremely short injection time is produced. During such an extremely short injection time Between them adversely affects the fuel regulation in the combustion chamber and thus also the quality of combustion. Have a positive effect.   Moreover, using a complex 3-port 2-position valve to control the injection process is Since it is extremely uneconomical, manufacturing known fuel injectors is laborious and costly.   Advantages of the invention   A fuel injection device for use in an internal combustion engine according to the present invention as set forth in claim 1. Has the following advantages over the conventional ones. That is, a well-known common tray The injection system of the injection type is improved, and the variable injection cross section in the injection valve enables The advantages of the high injection pressure provided can be fully utilized. this child Is easily possible by using an injection valve with a valve member that opens outwards. . A variable injection cross section can be controlled via the adjustable opening stroke of the valve member. Become.   The injection valve with the structure that opens outwards may in this case be infinitely controllable . For this purpose, the opening between the closing head and the valve seat can be controlled in relation to the valve member stroke. The annular gap forms the injection cross section. The injection cross section is preceded by the seal cross section Advantageously, it is controlled by means of a spool valve provided. The valve member of this spool valve is , For example, with a plurality of geometrically precisely defined injection openings. this Due to the arrangement of these injection openings, the overlap from the housing in relation to the opening stroke It is possible to adjust the precise injection cross section when the injection opening advances. These jets open The mouth is advantageously formed by two rows of injection holes located one above the other in the axial direction. is there. Both injection hole arrays are sequentially controlled to be opened during the opening stroke of the valve member. Thus, the regulation The valve member stroke controls the opening control of only the lower injection hole row near the combustion chamber. First of all, it is possible structurally to open only half of the total injection cross section. Become. In this case, it is possible for the valve member to stay in this prescribed intermediate position. Control means is provided. However, as an alternative, more rows of injection holes, It is also possible to provide a defined retention position for the valve member. Such injection holes are annular Better control of jet direction and jet flow of fuel to be injected compared to gap It has the advantage of being possible.   Thus, it is advantageous to open control only the injection cross section reduced by 50%. , Especially at low engine speeds and in the partial load range of the internal combustion engine to be fueled. Is advantageous. That is, despite the high injection pressure, the injection time is The advantage is that it can be adjusted to the optimum value for charge adjustment.   Thus, in the fuel injection device according to the present invention, the fuel injection device that can be freely set Fuel injection based on a combination of variable injection pressure and variable injection cross section. Can be optimally adjusted according to each operating point. Change of injection pressure is known In the high pressure collecting chamber, pressure control is performed.   Yet another advantage of the present invention is that it is simple to control the injection process in an injection valve. Obtained by using a 2-port 2-position valve. This 2-port 2-position valve is electromagnetic It is advantageous to operate with stones. But against this Alternatively, mechanical, hydraulic or pneumatic operation Known 3-port 2-position valves are also possible based on the known prior art.   The closing force applied to the valve member of the injection valve is due to the spring force or high pressure in the injection system. Therefore, it can be formed. To do this, the various features of the 2-port 2-position valve Various control concepts are possible. That is, the electromagnet operated a 2-port 2-position valve. For example, since it can be held open or closed with no current, The return chamber containing the end of the valve member on the combustion chamber side is located in the closed state of the injection valve. Is no pressure or pressure is applied. Open control of only the lower injection hole row The intermediate stopper that holds the valve member in the specified position is Formed as a closed controlled hole) or a mechanical stopper (second flange) It is advantageous if it is designed as a beating action. Use system pressure as closing force The valve member, a hydraulically adjustable closure head is used. Is advantageous to. The hydraulically adjustable axial extension of this closure head Through which a continuously adjustable stroke distance of the valve member is possible. Opening stroke of valve member The controlled variable for movement may be high fuel pressure in the injection system or 2 port 2 position. The position of the valve can be utilized.   These various control concepts are fueled. Has different advantages in relation to the preconditions imposed on the internal combustion engine . Therefore, only four embodiments are described in detail below. These fruits The features of the embodiments can be interchanged with one another and can be combined with one another. Book Other advantages and configurations of the inventive subject matter are described in the description of the embodiments, the drawings and the claims. It is described in.   Drawing   Below, four examples of the fuel injection device according to the present invention used in an internal combustion engine are illustrated. I will explain the surface in detail.   FIG. 1 is a currentless system utilizing the hydraulic closing force in the valve member of the injection valve. FIG. 2 shows the first embodiment provided with a 2-port 2-position solenoid valve that opens in a state, and FIG. FIG. 3 shows an enlarged sectional view of the range of the injection opening of the injection valve shown in FIG. 1, and FIG. 2 ports 2 closed in currentless state by utilizing hydraulic closing force in members Second embodiment with position valve and hydraulically adjustable closing piston FIG. 4 shows that the two-port two-position solenoid valve opened in the currentless state is closed. FIG. 5 shows a third embodiment in which the force is exerted by a closing spring, FIG. The two-position solenoid valve is closed without current, and the closing force is generated by the two-spring device. The 4th example which is formed is shown.   Description of the embodiment   Used in the internal combustion engine according to the first embodiment shown in FIG. The fuel injection device has a high-pressure fuel pump 1. This fuel high pressure pump 1 Is for feeding fuel from a low pressure chamber 3, preferably a fuel tank, via a pressure line 5 to a high pressure collecting chamber 7. Pump. From this high-pressure collecting chamber 7, a plurality of high-pressure pipe lines 9 corresponding to the number of injection points are provided. Injection valve 1 which extends into the combustion chamber of the internal combustion engine to be fueled It leads to 1. The injection valve 11 has a valve body 13, which is It has a central hole 15. A piston-shaped valve member 17 is axially provided in the hole 15. It is guided by. This valve member 17 projects from the hole 15 at the end on the combustion chamber side. It also has a closing head 19 which forms the valve closing member. Enlarged in Figure 2 On the side facing the valve body 13, the closing head 19 forms a sealing surface which forms a sealing edge. 21. Due to this sealing surface 21, the closing head 19 of the valve body 13 It cooperates with a valve seat surface 23 arranged on the end surface on the combustion chamber side. The closing head 19 is the valve member 1 7, the diameter of the hole 15 is enlarged, with an increased cross section compared to the piston shank of FIG. Into the hole 15 at the end face 25 on the side opposite to the combustion chamber. The formed pressure chamber 27 is partitioned. The pressure chamber 27 includes the wall of the hole 15 and the valve member shaft. Fuel passage provided in the valve body 13 via an annular gap 29 between It extends to 32. In this case, provided on the closing head 19, The cross section is preferably formed by the sleeve 26. is there. This sleeve 26 is fixed to the closure head 19 and runs along the wall of the hole 15. Slides tightly in the axial direction. The sleeve 26 forming the movable valve slider includes When two injection opening rows (injection hole rows) 28 that are vertically positioned in the axial direction are provided. It is advantageous. This injection opening row 28 is the first row when the valve member 17 advances from the hole 15. First, the first lower row near the combustion chamber is controlled to open after the specified idling stroke. , The upper second row, on the other hand, only operates after the valve member stroke has been carried out. The body 13 is arranged so as not to be released from the overlapping state with the hole wall of the body 13. Ring In order to supply fuel from the gap 29 to the injection opening 28, the valve member 17 and A notch 30 is provided between the sleeve 26 and the sleeve 26.   The annular gap 29 is oriented in the direction of the side facing away from the closure head 19 in the housing wafer. It is partitioned by the bus 31. In this housing web 31, the diameter of the holes 15 is reduced. A little, in which case the valve member 17 is guided in a close slidable manner. This howe Following the ging web 31, on the side opposite the combustion chamber, a new diameter enlargement of the hole 15 A back chamber 33 formed by the parts is provided. In the back chamber 33, the valve member 17 , The end on the side opposite to the combustion chamber projects. The back chamber 33 is the housing cover 3 Closed by 5. The end of the valve member facing away from the combustion chamber is It has a closing piston 37 which forms This closing piston 37 of the back chamber 33 Sliding tightly along the wall, thus the back chamber 33, the lower, combustion chamber forming the return chamber 39 A partial chamber on the side of the combustion chamber and a partial chamber on the side opposite to the combustion chamber, which forms the pressure release chamber 41. It is divided into and. In this case, the annular end surface on the combustion chamber side below the closing piston 37. Forms the pressure receiving surface 43 of the valve member 17 in the closing direction. This pressure receiving surface is closed. It is formed to be larger than the end surface 25 provided on the lid 19 and acting in the opening direction. You.   The opening stroke operation of the valve member 17 that supplies fuel to the injection valve 11 and opens outward In order to control the movement, the high-pressure line 9 branches into two partial lines near the injection valve 11. Have been. Of the two partial pipelines, the first partial pipeline 45 is not restricted and the fuel supply passage It opens at 32 and further opens at the pressure chamber 27. The second partial conduit 47 is the back chamber 3 3 is open to the return chamber 39. In this case, the second partial conduit 47 is By means of a two-port two-position valve 49, controllable by an electromagnet, inserted in the partial line It can be closed.   In order to release the pressure in the pressure release chamber 41 on the upper side of the back chamber 33, the pressure release pipe is released from the pressure release chamber 41. The path 51 extends and leads to the low-pressure chamber 3.   In order to control the opening stroke movement, the return chamber 39 located from the lower side to the closing control line is closed. 53 has been derived. The closed control line 53 has a closed piston 37. Closed by this closing piston 37 during the stroke movement of The back chamber 33 is opened so as not to be possible. Further, the closed control line 53 has 2 A control solenoid valve 55 formed as a port 2 position valve is inserted. This control power The magnetic valve 55 opens or closes the closed control line 53 toward the low pressure chamber 3. . The control solenoid valve 55 may be usable for multiple injection valves.   Further, from the return chamber 39, a throttle pipe line 59 having a throttle portion 57 is connected to the low pressure chamber 3. It has been derived. The opening of the throttle conduit 59 has a predetermined opening stroke distance. Arranged in the return chamber 39 such that it can be closed by the closing piston 37 after passing the separation Have been. In this case, this opening stroke position of the valve member 17 is the opening control of the lower injection hole row. Equivalent to God.   In order to limit the maximum opening stroke distance of the valve member 17, the stopper space is provided in the return chamber 39. Reeve 61 is inserted. The upper annular surface of the stopper sleeve 61 is closed. A stopper that cooperates with the pressure receiving surface 43 of the chain piston 37 is formed. This stopper The sleeve 61 has a through opening for the second partial line 47 and the closed control line 53. ing.   The fuel injection system according to the first embodiment shown in FIGS. 1 and 2 is constructed as follows. Move.   When the injection valve 11 is closed, the 2-port 2-position valve 49 is open ( Since the electromagnet is in a non-current state, the fuel formed in the high pressure collecting chamber 7 by the high pressure pump 1 The charge high pressure is propagated to the return chamber 39 of the back chamber 33. Created on the pressure receiving surface 43 of the closing piston 37. The high pressure used presses the sealing surface 21 of the valve member 17 against the valve seat surface 23. Injection valve 11 In order to open the valve, the 2-port 2-position valve 49 (energized state) and the back chamber 33 and high pressure gather The connection with the chamber 7 is cut off. The high pressure in the lower return chamber 39 is reduced via the throttle line 59. Pressed. In this case, this process, and eventually the progress of the opening stroke of the valve member 17, is restricted by the throttle 57. Can be adjusted by. Due to the reduction of the closing force acting on the valve member 17, The opening pressure formed in the force chamber 27 and acting on the valve member 17 via the end surface 25 is It is sufficient to lift 17 from the valve seat 23 and open the injection opening 28.   At this time, the valve member 17 first causes the closing piston 37 to close the throttle line 59, To the extent that the lower return chamber 39 closed at the time of forming a hydraulic stopper Only slides up to. At this position, the lower injection hole row is open controlled. valve When it is desired to continue the opening stroke of the member 17, the control solenoid valve 55 opens the closed control line 53. Since the pressure in the lower return chamber 39 is released to the low pressure chamber 3, the valve member 17 is released. Reaches the maximum opening distance until the closing piston 37 contacts the stopper sleeve 61. Can be achieved. At this time, the valve member 17 causes the second injection above the injection opening 28. The opening of the row of holes is also controlled. When you want to stop the retention of the valve member 17 in the intermediate position Promptly opens the closed control line 53, It is possible to achieve a fast maximum opening stroke.   In order to close the injection valve 11 again, the 2-port 2-position valve is opened again. In the lower return chamber 39, the fuel high pressure is formed again with the closed control line 53 closed. Is made. This high fuel pressure returns the valve member 17 to the valve seat 23.   The second embodiment shown in FIG. 3 is the only one in terms of controlling the opening stroke movement of the valve member. It differs from the first embodiment. Therefore, the description of the second embodiment relates to the constituent parts. Only done. The same components have the same reference numerals as in the first embodiment.   A second part branched from the high-pressure line 9 and opened to the return chamber 39 located on the lower side. A narrowing portion 63 is inserted in the pipe line 47. Furthermore, from the return room 39, The control pipe 65 is derived. This control line 65 is open to the low pressure chamber 3 and It can be closed by an electromagnetically controlled 2-port 2-position valve 49 inserted in the control line of is there.   The closing piston 37 is formed in two parts in the embodiment of FIG. Burning The upper piston part 67 farther from the baking chamber projects into the back chamber 33 of the valve member 17. The lower piston portion 69, which is rigidly connected to the end of the combustion chamber, is connected to the valve member shaft. It is slidably guided in the axial direction along the section. Between both piston parts 67 and 69 The chamber surrounded by forms a control chamber 71. this The control chamber 71 is a check valve which is supplied with fuel from the low pressure chamber 3 and which opens in the direction of the control chamber 71. It can be filled with fuel via a fuel line 73 with 75. Furthermore, the control room 71 Via a partial line 77 which is branched from the fuel line 73 and which can be opened by a control valve 79. Then, the pressure can be released to the low pressure chamber 3. Tightened between both piston parts 67, 69 The compression spring 81 presses both piston portions 67 and 69 in a state where the back chamber 33 is released. Move to the starting position.   The fuel injection system according to the second embodiment shown in FIG. 3 operates as follows.   2-port 2-position valve inserted in the control line 65 with the injection valve 11 closed Since 49 is closed (no current state), the fuel level is increased via the second partial line 47. Pressure is built up in the return chamber 39. This fuel high pressure causes the lower piston portion 69 to The member 17 is loaded in the closing direction. This closing force depends directly on the filling degree of the adjusting chamber 71. Or through a hydraulic cushion, the upper piston part fixed to the valve member As it is transmitted to the minute 67, the valve member 17 is held on the valve seat 23.   In order to open the injection valve 11, the 2-port 2-position valve 49 is opened (energized state). Then, the pressure in the return chamber 39 is released to the low pressure chamber 3. As a result, in the pressure chamber 27, The pressure acting on the valve member 17 in the opening direction lifts the valve member 17 from the valve seat 23. Will be enough for. In this case, this opening stroke movement is applied to the stopper sleeve 61. It continues until the side piston part 69 contacts. Variable stroke control of valve member The retention of the valve member 17 at the position where only the lower injection hole row is controlled to open is controlled by the adjustment chamber 7 Achieved by a specified filling of 1. For this, this hydraulic volume is minimal Fully filled via fuel line 73 for stroke, and for maximum stroke It is appropriately discharged through the control valve 79. In this case, by properly filling the control chamber 71 Also, multiple intermediate positions are possible. The injection valve 11 is closed by the 2-port 2-position valve 49. Is closed again. As a result, the return chamber 39 of the back chamber 33 is re-installed. And closing pressure is created and the valve member 17 is returned to the valve seat 23.   The third embodiment shown in FIG. 4 is the point of action of the closing force applied to the valve member 17. However, this is different from the above embodiment. In this case, the closing force is formed by the spring force You. For this purpose, the valve spring 83 is arranged in the back chamber 33. This valve spring 83 The spring receiver 85 arranged at the end of the valve member 17 on the side opposite to the combustion chamber, and the back chamber 3 It is clamped between an annular shoulder portion 87 which divides 3 on the combustion chamber side. This valve spring 83 , Which is formed in the pressure chamber 27, resists the high pressure of the fuel that loads the valve member 17 in the opening direction. Hold the valve member 17 in contact with the valve seat 23. From the back chamber 33, the pressure relief line 51 has been derived. This pressure release line 51 is open to the low pressure chamber 3, and Via a 2-port 2-position valve 49 inserted in line 51 It can be closed. Further, between the back chamber 33 and the 2-port 2-position valve 49, a high pressure pipe is provided. The second partial conduit 47 forming the connecting conduit between the conduit 9 and the back chamber 33 is the pressure relief conduit 51. It is open to. In this case, in the third embodiment of the fuel injection device according to the present invention, the second A narrowing point 57 is inserted in the partial pipe line 47 of FIG. In the third embodiment shown in FIG. The fuel injection device according to the present invention operates as follows.   In the closed state of the injection valve 11, the pressure release line 51 or the second partial line Since the 2-port 2-position valve 49 arranged at 47 is open (no current state), No high fuel pressure can be formed at 33. The valve spring 83 is provided in the pressure chamber 27 and is opened. Hold the valve member 17 on the valve seat 23 against the high fuel pressure acting on the valve member 17 in the release direction. ing. To open the injection valve 11, the 2-port 2-position valve 49 is connected to the back chamber 33. Since the pressure-release connection with the low-pressure chamber 3 is closed, the back chamber is connected via the second partial line 47. Within 33, the fuel high pressure of the injection system is formed. At this time, plunge into the back chamber 33 The combined pressing force acting on the valve member portion in the opening direction of the valve member 17 is Combined with the pressing force generated in 27, it is formed to be larger than the return force of the valve spring 83. As a result, the valve member 17 is lifted from the valve seat 23 and opens the injection opening. Ma Instead, the valve member 17 stays at a position where only the lower injection hole row is open-controlled. For example, due to the progressive characteristic line of the valve spring 83 or the specified idling stroke Can be achieved. In this case, the fuel high pressure in the high pressure collection chamber is used as the control pressure. It is.   In order to close the injection valve at the end of the injection process, the 2-port 2-position valve 49 is again Since the pressure release line 51 to the low pressure chamber 3 is opened, the fuel high pressure in the back chamber 33 is quickly released. Then, the valve spring 83 returns the valve member 17 to the valve seat 23.   In the fourth embodiment shown in FIG. 5, the second partial line 47 starting from the high-pressure line 9 Directly open to the back chamber 33, and in this case, the second partial conduit 47 is It can be closed by a 2-port 2-position valve inserted in the line 47. Release of the back chamber 33 The pressure is generated by the pressure release line 51 led out from the back chamber to the low pressure chamber 3. this In the fourth embodiment, the pressure release conduit 51 has a throttled portion 57.   The closing or restoring force applied to the valve member 17 is generated by the two spring device. It is. To this end, the valve member shaft portion that has entered the back chamber 33 is provided on the side opposite to the combustion chamber. An annular shape is provided between the spring bearing 85 arranged at the end portion and an annular shoulder portion 87 that partitions the back chamber 33. A step portion 89 is provided. A first valve is provided between the spring bearing 85 and the annular step 89. A spring 91 is tightened, and an annular step portion 89 and an annular shoulder portion 87 fixed to the housing are provided. A second valve spring 93 is clamped between the two, and in this case, the first valve spring 91 The spring rigidity is smaller than the spring rigidity of the second valve spring 93. This 4th In the embodiment, the first valve spring In order to adjust the forward stroke movement of the valve member 17 carried out against the spring force of 91, A sleeve 95 is fixed to the annular end surface of the spring receiver 85 on the spring side. This sleeve The end surface of 95 on the side opposite to the spring receiver 85 is an annular step 89 after the execution of the forward stroke movement. To contact. The sleeve 95 then shuts off the first valve spring 91 and the spring receiver 8 5 and the annular step 89 form a tight bond so that the opening stroke is continued. Then, only the second valve spring 93 acts. The retention in such an intermediate position is Alternatively, it can also be achieved without the sleeve 95. In this case, Both valve springs are effective.   The fuel injection system according to the fourth embodiment shown in FIG. 5 operates as follows.   With the injection valve 11 closed, the 2 port 2 inserted in the partial conduit 47 Since the position valve 49 is closed (no current is flowing), the back chamber 33 has a predetermined throttling point. Pressure is released to a specified pressure via a pressure release line 51 having 57. Valve member 1 7 is a valve seat 23 against the pressure in the pressure chamber 27 by the spring force of both valve springs 91 and 93. Held in contact with. If you want to inject, open the 2-port 2-position valve 49. Therefore, a high fuel pressure of the injection system is formed in the back chamber 33, and this high fuel pressure is As explained with reference to the figures, the valve member 17 is moved in the opening direction. In this case, first Small of the first valve spring 91 The forward stroke is carried out until the sleeve 95 contacts the annular step 89 against the spring force. You. This front stroke is for controlling the opening of the lower injection hole row provided in the valve member 17. Will be enough. In this position, the valve member 17 is the timing of the 2-port 2-position valve 49. It can be maintained to maintain a constant pressure in the back chamber 33 by means of the control of the pressure. Valve member When it is desired to control the opening of the entire injection cross section provided in 17, the pressure supply to the back chamber 33 is performed. Since the fuel supply is not interrupted, the fuel pressure in the back chamber 33 increases, in which case the valve member 17 Against the spring force of the second valve spring 93, the upper second injection hole array is also controlled to be opened. Can be moved to the position.   To continue to close the injection valve 11, the 2-port 2-position valve 49 is closed again. Therefore, the high pressure in the back chamber 33 is released to the low pressure chamber 3 via the pressure release line 51, and both valves are released. The springs 91 and 93 return the valve member 17 to the valve seat 23.   The operation of the 2-port 2-position valve 49 is performed by an electronic control device (not shown) in all the embodiments. (Not) controlled by electromagnets. In this case, the electronic control unit Handles a number of operating parameters of an internal combustion engine to be fueled in a known manner .   Therefore, the advantages of the "Common-Rail" type injection system are: It is structurally easy to combine with the advantages of the injection valve that is open to the outside. Therefore, it is possible to set variable injection start and At the same time as the end of injection and variable injection pressure are obtained, all of the internal combustion engine to be fueled It is also possible to freely adjust the variable injection cross section over the characteristic field . In this case, this fuel injection device can be easily controlled by a 2-port 2-position valve. You.

───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.6 識別記号 庁内整理番号 ＦＩ Ｆ０２Ｍ 63/02 9429−3Ｇ Ｆ０２Ｍ 63/02 Ａ (72)発明者 ラルフ マイアー ドイツ連邦共和国 73529 シュヴェービ シュ グミュント フランツ−チシュ−シ ュトラーセ 17 (72)発明者 シュテファン カムプマン ドイツ連邦共和国 70839 ゲルリンゲン パノラマシュトラーセ ９ (72)発明者 ウーヴェ ゴルドン ドイツ連邦共和国 71706 マルクグレー ニンゲン ダイムラーシュトラーセ 18 (72)発明者 アンドレアス クレー ドイツ連邦共和国 70499 シュツットガ ルト ダイデスハイマー シュトラーセ 61 (72)発明者 ネストル ロドリゲス−アマヤ ドイツ連邦共和国 70372 シュツットガ ルト デナーシュトラーセ 70─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. 6 Identification number Internal reference number FI F02M 63/02 9429-3G F02M 63/02 A (72) Inventor Ralph Meier 73529 Schwebisgmund Franz- Chisch-Schutrasse 17 (72) Inventor Stephan Kampumann Germany 70839 Gerlingen Panorama Strasse 9 (72) Inventor Uwe Gordon Germany 71706 Marc Gray Ningen Daimlerstrasse 18 (72) Inventor Andreas Kre Germany 70499 Stuttgart Deidesheimer Strasse 61 (72) Inventor Nestor Rodriguez-Amaya, Germany 70372 Stuttgart Denner Yutorase 70

Claims (1)

【特許請求の範囲】 １．内燃機関に用いられる燃料噴射装置であって、燃料高圧ポンプ（１）が設 けられており、該燃料高圧ポンプ（１）が、低圧室（３）から圧送管路（５）を 介して燃料を高圧集合室（７）に圧送するようになっており、該高圧集合室（７ ）が、高圧管路（９）を介して、燃料供給されるべき内燃機関の燃焼室に突入し た個々の噴射弁（１１）に接続されており、該噴射弁（１１）の開放運動および 閉鎖運動が、それぞれ噴射弁（１１）に設けられた高圧管路（９）に挿入された 制御弁によって制御される形式のものにおいて、噴射弁（１１）が、外方に向か って開く弁部材（１７）を有しており、該弁部材（１７）の、燃焼室の方向にお ける制御可能な開放行程運動により、噴射弁（１１）における可変の噴射横断面 が調節可能であることを特徴とする、内燃機関に用いられる燃料噴射装置。 ２．弁部材（１７）が、噴射弁（１１）の弁ボディ（１３）に設けられた孔（ １５）を通って案内される弁軸部を有しており、弁部材（１７）の燃焼室側の端 部が、前記孔（１５）から突出した、弁閉鎖部材を形成する閉鎖ヘッド（１９） を有しており、該閉鎖ヘッド（１９）の、弁ボディ（１３）に面した側が、シー ル縁部を形成するシール面（２１）を有しており、該シール面（２１）で前記閉 鎖ヘッド（１９）が、弁ボ ディ（１３）の燃焼室側の端面に配置された弁座面（２３）と協働するようにな っており、さらに、高圧管路（９）に接続された圧力室（２７）が設けられてお り、該圧力室（２７）が、弁部材（１７）の軸部と、前記孔（１５）の壁との間 に配置されており、前記圧力室（２７）が、前記閉鎖ヘッド（１９）によって燃 焼室に対して仕切られており、しかも弁部材（１７）に、弁座面（２３）と弁軸 部との間で仕切られた、軸方向を向いた受圧面（２５）が配置されている、請求 項１記載の燃料噴射装置。 ３．噴射弁（１１）における噴射横断面が、スプール弁装置により制御される ようになっており、該スプール弁装置の可動のスプール部分が弁部材（１７）と 共に移動させられるようになっており、スプール弁装置の、噴射横断面を形成す る開放横断面が、弁座面（２３）の上流側に位置している、請求項２記載の燃料 噴射装置。 ４．開放方向での弁部材（１７）の規定の行程が実施された後でしか、噴射横 断面が開制御されないようになっている、請求項３記載の燃料噴射装置。 ５．弁部材（１７）の一部が、可動のスプール部分として形成されており、該 スプール部分が、前記閉鎖ヘッド（１９）の範囲で前記孔（１５）に案内されて いて、その全周にわたって分配された噴射開口（２８）の、軸方向で上下に位置 する２つの噴射開口列を有 しており、該噴射開口（２８）が、前記圧力室（２７）を起点として配置されて いて、しかも軸方向で互いにずらされた噴射開口（２８）の流出開口が、弁部材 （１７）の開放行程運動時に、弁座面（２３）によって形成された制御縁部で前 記孔（１５）との重なりからの進出により順次に燃焼室に向かって開制御可能と なるように配置されている、請求項３記載の燃料噴射装置。 ６．弁部材（１７）の、燃焼室とは反対の側の端部が、操作部分に結合されて おり、該操作部分が、弁ボディ（１３）に設けられた、高圧管路（９）に接続可 能な背室（３３）を仕切っており、少なくとも作用接続で該背室（３３）の高圧 充填または高圧放圧を介して、弁部材（１７）の開放運動および／または閉鎖運 動が制御弁によって制御可能である、請求項２記載の燃料噴射装置。 ７．噴射弁（１１）の開閉運動を制御する制御弁が、高圧管路に、電気制御さ れる方向切換弁（４９）として形成されている、請求項１記載の燃料噴射装置。 ８．電気制御される方向切換弁（４９）が、電磁弁として形成されている、請 求項７記載の燃料噴射装置。 ９．噴射弁（１１）が２つの部分管路を介して高圧集合室（７）に接続されて おり、両部分管路のうち、第１の部分管路（４５）が、弁部材（１７）と前記孔 （１５）との間に形成された、開放方向で弁部材（１７）に作用する圧力室（２ ７）を常時、高圧集合室（７）に接続しており、第２の部分管路（４７）が、前 記圧力室（２７）と隔離された戻し室（３９）に開口しており、該戻し室（３９ ）への、高圧下にある燃料の充填が、電気制御される方向切換弁（４９）として 形成された制御弁によって制御可能である、請求項６記載の燃料噴射装置。 10．弁部材（１７）の操作部分が、閉鎖ピストン（３７）を有しており、該閉 鎖ピストン（３７）の燃焼室側の端面が、受圧面（４３）を有しており、該受圧 面（４３）を介して、弁部材（１７）が閉鎖方向で負荷可能であり、前記受圧面 （４３）が、弁部材（１７）に設けられた、開放方向で作用する受圧面（２５） よりも大きく形成されており、前記閉鎖ピストン（３７）が、前記背室（３３） の壁に沿って密に滑動するようになっていて、前記背室（３３）を、燃焼室とは 反対の側の上側の、放圧された放圧室（４１）と、弁ボディ（１３）に設けられ た、燃焼室寄りの下側の戻し室（３９）とに分割している、請求項９記載の燃料 噴射装置。 11．電気制御される方向切換弁（４９）が、高圧管路（９）の第２の部分管路 （４７）に挿入されている、請求項１０記載の燃料噴射装置。 12．前記方向切換弁（４９）が、２ポート２位置弁 として形成されており、前記戻し室（３９）が、絞り（５７）を有する絞り管路 （５９）を介して常時、低圧室（３）に接続されている、請求項１１記載の燃料 噴射装置。 13．前記閉鎖ピストン（３７）の行程運動時に該閉鎖ピストン（３７）によっ て閉鎖不可能な閉制御管路（５３）が、前記戻し室（３９）から低圧室（３）に 導出されており、該閉制御管路（５３）が、電気的に制御される弁（５５）によ って開閉可能である、請求項１０記載の燃料噴射装置。 14．弁部材（１７）の、前記噴射開口（２８）のうちの燃焼室側の下側の噴射 開口列を開制御する開放行程距離が達成された後に、前記戻し室（３９）から低 圧室（３）へ通じた前記絞り管路（５９）が、前記閉鎖ピストン（３７）によっ て閉鎖される、請求項１２記載の燃料噴射装置。 15．前記戻し室（３９）に行程ストッパ（６１）が設けられており、該行程ス トッパ（６１）に、最大開放行程運動の実施後に前記閉鎖ピストン（３７）の受 圧面（４３）が当接するようになっている、請求項１０記載の燃料噴射装置。 16．高圧管路（９）の第２の部分管路（４７）に絞り個所（６３）が配置され ており、前記戻し室（３９）から閉制御管路（６５）が導出されて低圧室（３） に通じており、該閉制御管路（６５）が、弁部材（１ ７）の開閉運動を制御する方向切換弁（４９）によって閉鎖可能である、請求項 １０記載の燃料噴射装置。 17．下側の戻し室（３９）の方向での前記閉鎖ピストン（３７）の軸方向の延 在長さが可変である、請求項１５記載の燃料噴射装置。 18．前記閉鎖ピストン（３７）が、２つのピストン部分から形成されており、 両ピストン部分のうち、燃焼室とは反対の側の上側のピストン部分（６７）が、 弁部材（１７）に固く結合されており、燃焼室寄りの下側のピストン部分（６９ ）が、軸方向で移動可能に弁部材（１７）の軸部に案内されており、両ピストン 部分（６７，６９）の間に調節室（７１）が取り囲まれており、該調節室（７１ ）から、電気的に制御される弁（７９）によって開放可能な燃料管路（７３）が 導出されて、低圧室（３）に通じており、さらに前記調節室（７１）に、両ピス トン部分（６７，６９）の間に緊定された圧縮ばね（８１）が配置されている、 請求項１７記載の燃料噴射装置。 19．弁部材（１７）の軸部が、前記孔（１５）の一部に密に案内されており、 該孔（１５）の一部が、前記背室（３３）を仕切っており、弁部材（１７）の、 燃焼室とは反対の側の、前記背室（３３）に突入した端部が、ばね受け（８５） を有しており、該ばね受け（８５）と、前記孔（１５）から前記背室（３３）へ の移行部に形成された環状肩部（８７）との間に、弁 ばね（８３）が緊定されており、該弁ばね（８３）が、弁部材（１７）を閉鎖方 向で負荷している、請求項９記載の燃料噴射装置。 20．前記第２の部分管路（４７）に絞り個所（５７）が設けられており、前記 背室（３３）から低圧室（３）に通じた放圧管路（５１）が前記第２の部分管路 （４７）から分岐されており、該放圧管路（５１）に、弁部材（１７）の開放運 動を制御する、電気的に制御される方向切換弁（４９）が挿入されている、請求 項１９記載の燃料噴射装置。 21．弁部材（１７）の、燃焼室とは反対の側の端部が、ばね受け（８５）を有 しており、該ばね受け（８５）と、前記背室（３３）の、弁ボディ（１３）に設 けられた前記孔（１５）の環状肩部（８７）によって形成された壁との間に、２ つのばね（９１，９３）から形成された弁ばね装置が緊定されており、該弁ばね 装置が、弁部材（１７）を閉鎖方向で負荷しており、さらに前記弁ばね装置が、 弁部材（１７）の開放行程運動時に順次に有効となる、請求項９記載の燃料噴射 装置。 22．噴射弁（１１）の開放運動を制御する前記方向切換弁（４９）が、前記背 室（３３）に開口した第２の部分管路（４７）に挿入されており、低圧室（３） へ通じた、絞り個所（５７）を有する放圧管路（５１）が前記背室（３３）から 導出されている、請求項１ ９または２１記載の燃料噴射装置。[Claims]   1. A fuel injection device used in an internal combustion engine, comprising a fuel high pressure pump (1). The fuel high-pressure pump (1) is connected to the low-pressure chamber (3) through the pumping line (5). The fuel is pressure-fed to the high pressure collecting chamber (7) via the high pressure collecting chamber (7). Via the high pressure line (9) enters the combustion chamber of the internal combustion engine to be fueled. Connected to the individual injection valve (11) and the opening movement of the injection valve (11) and A closing movement was inserted in the high-pressure line (9) provided in each injection valve (11) In the type controlled by a control valve, the injection valve (11) is directed outwards. Has a valve member (17) that opens toward the combustion chamber of the valve member (17). Variable injection cross-section in the injection valve (11) due to controllable opening stroke movement Is an adjustable fuel injector for an internal combustion engine.   2. The valve member (17) is a hole (() formed in the valve body (13) of the injection valve (11). 15) has a valve shaft portion which is guided through, and the end of the valve member (17) on the combustion chamber side. A closure head (19), a part of which projects from the hole (15) and forms a valve closure member. And the side of the closure head (19) facing the valve body (13) is Has a sealing surface (21) forming a rim edge, and the sealing surface (21) closes the seal. The chain head (19) is So as to cooperate with the valve seat surface (23) arranged at the combustion chamber side end surface of the disk (13). In addition, a pressure chamber (27) connected to the high pressure line (9) is provided. The pressure chamber (27) between the shaft of the valve member (17) and the wall of the hole (15). And the pressure chamber (27) is ignited by the closure head (19). It is partitioned from the baking chamber, and the valve member (17) has a valve seat surface (23) and a valve shaft. An axially directed pressure-receiving surface (25), which is partitioned between the parts, is arranged. Item 1. The fuel injection device according to item 1.   3. The injection cross section in the injection valve (11) is controlled by the spool valve device. And the movable spool portion of the spool valve device serves as a valve member (17). It is adapted to be moved together and forms the injection cross section of the spool valve device. 3. The fuel according to claim 2, wherein the open cross section is located upstream of the valve seat surface (23). Injection device.   4. Only after the prescribed stroke of the valve member (17) in the opening direction has been carried out The fuel injection device according to claim 3, wherein the cross section is not controlled to be opened.   5. A part of the valve member (17) is formed as a movable spool part, A spool portion is guided in the hole (15) in the area of the closing head (19). And located axially above and below the injection openings (28) distributed over its entire circumference. Has two injection aperture rows The injection opening (28) is arranged with the pressure chamber (27) as a starting point. And the outflow openings of the injection openings (28) axially offset from each other are During the opening stroke movement of (17), the control edge formed by the valve seat surface (23) It is possible to control the opening sequentially toward the combustion chamber by advancing from the overlap with the writing hole (15). The fuel injection device according to claim 3, wherein the fuel injection device is arranged so that   6. The end of the valve member (17) facing away from the combustion chamber is connected to the operating part. And the operating part can be connected to the high pressure line (9) provided in the valve body (13). Partition the active back chamber (33), and the high pressure of the back chamber (33) is at least operatively connected. Opening and / or closing movement of the valve member (17) via filling or high pressure relief. The fuel injector according to claim 2, wherein the movement is controllable by a control valve.   7. A control valve for controlling the opening and closing movement of the injection valve (11) is electrically controlled in the high pressure line. 2. The fuel injection device according to claim 1, which is embodied as a directional control valve (49).   8. The electrically controlled directional control valve (49) is embodied as a solenoid valve, The fuel injection device according to claim 7.   9. The injection valve (11) is connected to the high pressure collecting chamber (7) via two partial lines The first partial conduit (45) of the two partial conduits is the valve member (17) and the hole. A pressure chamber (2) formed between the pressure chamber (2) acting on the valve member (17) in the opening direction. 7) is always connected to the high pressure collecting chamber (7) and the second partial conduit (47) is The return chamber (39) is isolated from the pressure chamber (27), and the return chamber (39) is opened. ) Is filled with fuel under high pressure as an electrically controlled directional control valve (49). 7. The fuel injection device according to claim 6, which is controllable by means of a formed control valve.   Ten. The operating part of the valve member (17) has a closing piston (37), The end surface of the chain piston (37) on the combustion chamber side has a pressure receiving surface (43). A valve member (17) is loadable in the closing direction via a surface (43), said pressure receiving surface (43) is a pressure receiving surface (25) provided on the valve member (17) and acting in the opening direction. The closing piston (37) is larger than the back chamber (33). The back chamber (33) is designed to slide closely along the wall of the Provided on the opposite side, on the upper side, in the pressure relief chamber (41) and in the valve body (13) The fuel according to claim 9, which is divided into a lower return chamber (39) near the combustion chamber. Injection device.   11. The electrically controlled directional control valve (49) is connected to the second partial line of the high pressure line (9). The fuel injection device according to claim 10, which is inserted in (47).   12. The direction switching valve (49) is a 2-port 2-position valve. And the return chamber (39) has a throttle line (57). 12. Fuel according to claim 11, which is always connected to the low-pressure chamber (3) via (59). Injection device.   13. By the closing piston (37) during the stroke movement of the closing piston (37) A closed control line (53) that cannot be closed from the return chamber (39) to the low pressure chamber (3). The closed control line (53) is derived by an electrically controlled valve (55). The fuel injection device according to claim 10, which can be opened and closed.   14. Injection on the lower side of the valve member (17) on the combustion chamber side of the injection opening (28) After the opening stroke distance for controlling the opening of the opening row is reached, the return chamber (39) is lowered. The throttle line (59) leading to the pressure chamber (3) is closed by the closing piston (37). 13. The fuel injector of claim 12, wherein the fuel injector is closed.   15． A stroke stopper (61) is provided in the return chamber (39), and the stroke stopper (61) is provided. The topper (61) receives the closing piston (37) after performing the maximum opening stroke movement. 11. The fuel injection device according to claim 10, wherein the pressure surface (43) abuts.   16. A throttling point (63) is arranged in the second partial line (47) of the high-pressure line (9). The closed control line (65) is led out from the return chamber (39) to enable the low pressure chamber (3). To the valve member (1). 7. It can be closed by means of a directional control valve (49) controlling the opening and closing movements of 7). 10. The fuel injection device according to item 10.   17． Axial extension of said closing piston (37) in the direction of the lower return chamber (39) The fuel injection device according to claim 15, wherein the existing length is variable.   18． Said closing piston (37) is formed from two piston parts, Of the two piston parts, the upper piston part (67) on the side opposite to the combustion chamber is It is rigidly connected to the valve member (17) and has a lower piston part (69) close to the combustion chamber. ) Is guided by the shaft of the valve member (17) so as to be movable in the axial direction. A control chamber (71) is enclosed between the parts (67, 69) and the control chamber (71 ) From a fuel line (73) that can be opened by an electrically controlled valve (79). It is led out and leads to the low pressure chamber (3), and further to the adjustment chamber (71), both pistons are connected. A tensioned compression spring (81) is arranged between the tongues (67, 69), The fuel injection device according to claim 17.   19. The shaft portion of the valve member (17) is closely guided in a part of the hole (15), A part of the hole (15) partitions the back chamber (33), and the valve member (17) is The end projecting into the back chamber (33) on the side opposite to the combustion chamber has a spring bearing (85). The spring receiver (85) and the hole (15) to the back chamber (33). Between the annular shoulder (87) formed at the transition of the valve A spring (83) is tightened so that the valve spring (83) closes the valve member (17). 10. The fuel injection device according to claim 9, which is loaded in the opposite direction.   20. A narrowing portion (57) is provided in the second partial pipeline (47), The pressure relief conduit (51) leading from the back chamber (33) to the low pressure chamber (3) is the second partial conduit. (47) is branched and the valve member (17) is opened to the pressure relief line (51). An electrically controlled directional control valve (49) for controlling movement is inserted. Item 20. The fuel injection device according to item 19.   twenty one. The end of the valve member (17) facing away from the combustion chamber has a spring bearing (85). The spring receiver (85) and the valve body (13) of the back chamber (33). Between the hole formed by the annular shoulder (87) of the hole (15), 2 A valve spring device formed of three springs (91, 93) is clamped The device loads the valve member (17) in the closing direction, and the valve spring device further comprises: 10. The fuel injection according to claim 9, which is activated sequentially during the opening stroke movement of the valve member (17). apparatus.   twenty two. The direction switching valve (49) for controlling the opening movement of the injection valve (11) is The low pressure chamber (3) is inserted into the second partial pipe line (47) opened to the chamber (33). From the back chamber (33) is provided a pressure relief line (51) having a restriction point (57) leading to Claim 1 has been derived The fuel injection device according to 9 or 21.
JP8524601A 1995-02-15 1996-01-19 Fuel injection device used for internal combustion engine Abandoned JPH09512616A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19504849A DE19504849A1 (en) 1995-02-15 1995-02-15 Fuel injection device for internal combustion engines
DE19504849.0 1995-02-15
PCT/EP1996/000230 WO1996025596A1 (en) 1995-02-15 1996-01-19 Fuel injection device for internal combustion engines

Publications (1)

Publication Number Publication Date
JPH09512616A true JPH09512616A (en) 1997-12-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
JP8524601A Abandoned JPH09512616A (en) 1995-02-15 1996-01-19 Fuel injection device used for internal combustion engine

Country Status (7)

Country Link
US (1) US5823161A (en)
EP (1) EP0779949B1 (en)
JP (1) JPH09512616A (en)
KR (1) KR970702428A (en)
CN (1) CN1062331C (en)
DE (2) DE19504849A1 (en)
WO (1) WO1996025596A1 (en)

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Also Published As

Publication number Publication date
DE59605715D1 (en) 2000-09-14
US5823161A (en) 1998-10-20
EP0779949A1 (en) 1997-06-25
EP0779949B1 (en) 2000-08-09
KR970702428A (en) 1997-05-13
DE19504849A1 (en) 1996-08-22
WO1996025596A1 (en) 1996-08-22
CN1062331C (en) 2001-02-21
CN1145652A (en) 1997-03-19

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Effective date: 20040414